Utilizing expansive energy.



W. C. BROWN. UTILIZING EXPANSIVE ENERGY.

I APPLICATION FILED DEC. 6. 1912. 1,224,705. Patented Ma 1, 1917.

3 SHEETS-SHEET I.

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WITNESSES:

IN VIZN TOR. Maw MAP 6 By M & ATTORNEY.

W. C. BROWN.

UTILIZING EXPANSIVE ENERGY.

APPLICATION FILED DEC. 6. l9l2.

1,224,705. Patented May 1, 1917.

3 SHEETS-SHEET 2.

WI TIIESSES ATTORNEY.

INVENTOR w. 0. BROWN.

UTlLiZlNG EXPANSIVE ENERGY.

APPLICATION FILED DEC-6. 1912.

' 1,224,705. v Patented May1,1917.

3 SHEETS-SHEET 3- WITNESSES. I INVENTOR.

A TTORN E Y.

WITED STATEfl PATENT @FWIQE.

WILLIAM CLINTON BROWN, OF SYRACUSE, NEW YORK, ASSIGNOR TO HUIVIPHREY GAS PUMP GOMPANY, A CORPORATION OF NEW YORK.

UTILIZING nXrANsIvE ENERGY.

Specification of Letters Patent.

Patented May 1., 1917.

To all whom it may concern Be it known that I, l/VILLIAM CLINTON BROWN, a citizenof the United States, residing at Syracuse, in the county of Onondaga, State of New York, have invented new and useful Improvements in Utilizing Expansive Energy, of which the following is a specification.

This invention relates to improvements in high duty pumping and compressing of fluids. It comprises a new and useful com.- bination of methods and means employed in the uni -flow steam cylinder and the Humphrey system of pumping and compressing. It combines, for new and useful results, methods of raising, compressing and forcing fluids, employing no flywheels, but.

suitably proportioned reciprocating masses of the fluids themselves,- with a power cycle employing high compression, full expansion, good vacuum, and uni-directional flow of a primary mediumsupplied at high pressure. The combination results in a method of complete simplicity and high economy for utilizing expansive energy. In former arrangements for pumping and compressing by expansive energy, high duty and good economy have required both complicated and expensive construction. The great majority of direct acting pumps and compressors, have sacrificed economy to simplicity.- The advantages of the system, which utilizes momentum and inertia of reciprocating masses of fluid in both directions to allow full eXpansion, to entrain fresh fluids, and fresh primary medium, and to compress combustible charges, have been applied heretofore only to internal combustion cycles. These cycles have never proved so reliable nor so generally applicable as those employing a medium supplied at high pressure, as in the case of steam. Moreover, internal combustion demands more expensive construction of the power cylinders than mediums supplied at high pressure from external sources, and entails high maintenance and operating costs.

Engines, compressors and pumps built with uni-flow'cyli'nders have even suffered failures in connecting rods, cranks, bearings and other parts subject to strains accompanying high compression. Yet this compression has been found to be as beneficial to the thermal efliciency of a uni-flow cycle as to those of internal combustion. But its disadvantages make the design and construction of engines with uni-flow cylinders both as difficult and as expensive as in the case of internal combustion engines. These difficulties, however, have been to great extent ofl'set by the reliability and high even oiny of the uni-flow cycle.

The object of the invention, therefore, is to secure, by combination, the advantages of the uni-flow cycles with those of the previously described systems of pumping, compressing and generating power, without the disadvantages of either. It is my purpose by this combination to achieve methods and means for utilizing the expansive energy of steam or other medium for raising, forcing and compressing fluids, and for the generation of power, with high etliciency, good economy, complete simplicity, absolute reliability, and broad range of application to commercial service.

Referring to the drawings which illustrate merely by way of example the principle of my invention and suitable appara tus for effecting it Figure I. shows a section of such apparatus in elevation.

Fig. II represents a typical diagram of a power cycle.

Fig. III is a plan showing a modified arran ement of such apparatus.

Fig. IV is a sectional elevation of Fig. III.

Fig. V shows another modification employing double acting cylinders.

Fig. .VI shows a further modification suitable, forcompression of elastic fluids.

Fig. VII shows a uni-flow compressor cylinder.

- Similar numerals are used to designate similar parts throughout the several views.

Referring to Fig. I:-

g 1 designates a piston which moves in a power cylinder 3. 2 represents a plunger connected therewith and operating in a pump chamber 41-. 5 is a suitably controlled passage for admission of working medium such assteam at high pressure. 6 represents a heating jacket about the head of cylinder 3 and supplied with heated primary medium from passage 5 under control of valve 7. 8 is a partial acket for extending the heating effect through the admission period of the cycle. 9 is a separate exhaust passage and cooling belt in communication with the cylinder 3 by means of ports 0verrun and controlled by piston 1. At 10 are shown valve controlled inlets for fluid in the vicinity of pump chamber 4: from a compensating suction vessel 11 which maintains a nearly uniform flow in suction pipe 12 from the supply level 13. In free communication with said pump chamber and suction inlets are play pipes and cylinders for constrainment of reciprocating masses and columns such as 1 1 and 16. High pressure dis charge outlets are shown at 15, between columns 14 and 1(3, and a relatively low pressure ovcrllow outlet at 18. A compensating delivery vessel, or high pressure accumulator 20 controls the discharge through valve 21. 17 designates the upper extremity of the reciprocating columns and 19 a shutoff valve on the low pressure connection to discharge main 26.

The complete arrangement here shown is that suitable for raising and forcing water to different heads or pressures interchangeably. It is particularly adapted to municipal service as a means of water supply and high pressure fire service together in one unit.

Fig. II represents a typical cycle such as is carried out in cylinder 3 of Fig. I. It is a diagram of pressures and cylinder displacements, or volumes, on which areas represent quantities of energy, or work. OP is the axis of absolute pressures; OV that of displacements, or volumes. AT is the line representing the pressure of the atmos phere for all volumes. In the power cycle, such as would be traced by a pressure indicator on cylinder 3, BC represents a period of admission of primary medium such as steam or other heated or compressed fluid at high pressure. At C the supply is cut off and expansion CD takes place. At D exhaust outlets are opened and the expanded working medium expelled. The return stroke of piston 1 compresses whatever fluid remains in the cylinder after exhaust nearly up to the pressure of admission, thereby absorbing the energy of the reciprocating masses and bringing them to rest at the proper point. This compression EB also raises the temperature from that of cool exhaust to that of the warm supply.

Referring to the arrangement shown in Fig. I and the cycle diagram in Fig. II, the operation is as follows With the parts in the positions and relations shown, steam or other medium is admitted by passage 5 at high pressure to act upon the working face of piston 1. This high pressure, transmitted by plunger 2 to the reciprocating masses in play pipes 1st and 16 causes acceleration of these columns against the force of gravity and the pressure of atmosphere or other medium acting at their upper extremities. Under this acceleration the reciprocating bodies move outward and upward, admission is cut off in passage 5, (BC in Fig. II), expansion follows (CD) and the masses gain momentum. This serves to complete the expansion even below atmospheric pressure, so that when piston 1 and plunger 2 come to rest during exhaust (DE), further movement of columns 14; and 16 causes a low pressure to prevail in the vicinity of the inlets 10, with the result that a fresh increment of the fluid to be pumped is entrained. Meanwhile a similar volume of fluid has been discharged at a greater head or pressure. In normal operation of this apparatus, valve 21 is closed, valve 19 opened, and water or other fluid is discharged into main 26 by simply overflowing the upper end of the play pipe at 18. When higher pressure is desired, for fire fighting or other purposes, valve 19 is closed and valve 21 opened. This brings into play the discharge valves at 15 which are opened during the first acceleration of the columns by the dynamic pressure due to the inertia of column 16. This pressure, being much greater than that due to the weight of column 16 alone, is suiiicient to raise the pressure in main 26 materially. Any change in pressure or demand is automatically met by change in the length and mass of column 16 under the influence of a dynamic balance between suction and discharge, as explained in the copending application of C. C. Trump, Serial No. 735,240, filed Dec. 6, 1912, for utilizing dynamic pressure.

Having completed the power stroke the reciprocating columns are in an unbalanced state under the forces of gravity and pressure at 17. These forces accelerate the col umns downward and the piston 1 inward. The first short movement of piston 1 closes ports between the cylinder and the exhaust chamber 9 with the result that whatever medium remains in cylinder 3 is compressed according to line EB of Fig. II. This compression, in absorbing the kinetic energy of the moving masses, is carried to a pressure much above that corresponding to the hydraulic head of the columns above cylinder 3 before they are brought to rest. The final pressure should be slightly less than the sup ply pressure of the primary medium. It de pends upon the energy absorbing characteristics of the medium compressed and upon the forces propelling the reciprocating masses and the distances through which they act during compression. From a balance of energies, according to well known laws of hydraulics, kinetics and thermodynamics, may be calculated the actual compression pressure.

Before the end of thecompression stroke at an interval sufficient to allow for operation of valves suitable means are actuated to cause admission of primary medium such as steam or other elastic fluid at high pressure. This admission is continued according to the line B0 of Fig. II and the reciprocating masses are again accelerated outward and upward on a new cycle. Thus the cycle repeats itself periodically.

Figs. III and IV, in plan and sectional views respectively, show an arrangement which differs from that of Fig. I in that the reciprocating masses, instead of oscillating under displacements by power impulses against the returning force of gravity and elastic cushion accumulators, are interposed between two power actuators and cylinders whereby ieciprocations are produced by alternate compressions and expansions, every stroke being a power stroke.

In Figs. III and IV, 1 and 1 designate the two actuating pistons. 2 and 2 are their respective plungers. 3 and 3 are two uniflow cylinders: in which inlet and exhaust passages are at opposite ends, the latter being in the form of ports controlled by pistons 1 and 1. 5 and 5 designate valve con trolled admission passages for steam or compressed elastic iiuid at high pressure. 6 shows a part of such passages which acts as a heating jacket around valves and head only. This is the only jacket required for the highest economy with compressed air or highly superheated steam. In each pump chamber 4 and 4 are situated valve controlled inlets for fluid to be pumped or compressed. From these pump chambers lead play pipes for constraining columns 14 and 16. These play pipes establish free communication between the two or more pump chambers themselves, and also between the inlets and suitably placed and controlled discharges such as 15. An elastic cushion accumulator 20 is here shown for compensating fluctuations of pressure in the play pipes and maintaining a nearly steady discharge through main 21. A similar vessel is shown on the suction inlets at 11, and this serves to draw fluid from a source of supply 12 in a nearly steady flow. Both sets of inlets may be connected to one supply main. In this arrangement the cylinders are shown single acting. In certain cases it is of advantage to apply double acting cylinders to this arrangement as well as to that shown in Fig. V.

The cycle of operations in each cylinder as shown in Fig. III is the same as that described for Fig. I and shown in Fig. II. The high pressure period of the cycle occurs in each cylinder alternately, and the excess of energy in the first part of the power stroke in one is transmitted and distributed to perform the excess of work at the end of the compression in the other by the inertia, velocity and momentum of the reciprocating columns. Fluid is discharged during the first part of each power stroke by dynamic pressure, and this helps to absorb part of the excess energy. Fluid is entrained in equal increments by momentum of the columns after the actuating plungers have come to rest at the instant of exhaust. In this arrangement, therefore, it will be seen that a plurality of cylinders in which expansive energy is utilized with the least possible loss of heat from the expansive medium to the cylinder surfaces secures great advantages of simplicity and effectiveness by combination with reciprocating masses consisting in part of fluids to be pumped or compressed. This arrangement has the additional advantage that the distribution of functional energy by the moving columns complete for each single stroke so that no further losses occur from storage of energy in gravity accumulatdrs, elastic cushions and velocities of idle return strokes. This arrangement, therefore, is one which most com pletely and directly utilizes expansive energy.

A still more compact and powerful arrangement is shown in Fig. V. A double faced piston 1, operating in a double ended cylinder 3, is direct connected to a double acting plunger 2 working between two separate pump chambers 4 and 4. 5 and 5 designate suitably controlled inlets for primary medium at opposite warm ends of cylinder 3. Suitable heating jackets for use with saturated steam or other vapor are shown at 6, 6 8 and 8 with controlling valves 7 and 7. The central cooling and exhaust belt 9 leads from ports in the wall of cylinder 3 overrun and controlled by piston 1 to an exhaust chamber or condenser 12. 10 and 10 are valve controlled inlets for fluid, in the vicinity of plunger 2, in pump chambers 4 and 4 respectively. In close communication with these inlets are one or more suction vessels such as 11 whereby the supply of fluid is drawn through a surface condenser or exhaust cooler such as 12. In direct communication with each of the pump chambers 4 and 4 is a play pipe of suitable proportions leading to the various discharge outlets and inclosing the reciprocating columns 14, 14, 16 and 16*. High pressure discharge outlets such as 15 valve controlled, are properly located between columns 14 and 16. Under the equalizing efiect of one or more accumulators or elastic cushions such as 20 fluid is discharged at a nearly steady high pressure by way of main 21. Low pressure discharges are provided by collecting overflow from the tops of play pipes 17 and 17 in open tanks or closed vessels such as 18 for delivery into low pressure main 19. This arrangement is that well suited to pumping, interchangeably at low or high pressure, non-elastic fluids such as water. It is obvious, however, that the apparatus may be arranged for discharge at high pressures or low pressures separably. Although the combination arrangement is a part of my invention, 1 do not confine myself to the use of an intercl'iangeable arrangement such as is shown in Figs. I and V in all cases.

Two separate and distinct columns reciprocated by one double acting plunger and power cylinder are desirable when, for high e'tliciency, the power cylinders are exhausted into a condenser or other means of maintaining high vacuum or low absolute pressure. Unless the pressure of the atmosphere balanced in some such way, the energy available by atmospheric pressure, in addition to the working head, as explained in connection with Fig. I, acting upon the small quantity of expansive medium remaining in the cylinder, will cause excessive compression. A single acting arrangement can be compensated for atmospheric pressure it true, by maintaining a low absolute pressure or vacuum, on the face of the piston 1 opposite the working face, or by interposing a separate balancing piston or other suitable means. The double acting arrangement, however, besides utilizing more readily existing types and designs of apparatus, overcomes such difliculties due to extreme difference of pressures and allows an extremely compact and convenient construction.

The cycles of operation in each end of cylinder 3 are identical with those typified by Fig. II. In the pump chambers 4i and 4s, however, entrainment of fresh fluid is effected not only by energy stored in momentum of columns 14: and 16 after plunger 2 has come to rest at the end of its stroke, but in addition by the power impulse which starts the return stroke of the pump plunger. Under certain conditions and suitable proportions of the reciprocating columns this even eilects delivery of volumes of fluid greater than. those represented by the displacements of the plunger. The advantages of the double acting uniflow cylinder and of the double acting arrangement of a system of pumping or compressing by reciprocating masses gain considerably in effectiveness and simplicity by combination.

For blowing or compressing elastic fluids such as air an arrangement of chambers such as that shown in Fig. V1 is provided. A pair of such compressor chambers as 22 and 22 are provided with a suitable num ber of inlets and outlets for elastic fluid properly controlled by valves such as inlets 23 and 23, outlets 2a and 2a. The discharge outlets of such a pair may open into a common discharge pipe 25, leading to a separating receiver. For it is desirable to discharge with the elastic fluid small portions of cooling liquid such as water for absorbing heat of compression and so to reduce the work required by approach to isothermal conditions. Liquid is then entrained near the actuating plunger from the receiver or other source for circulation and dynamic regulation.

For high pressure compressing such cham bers as 22 and 22 should be connected to the play pipes near the pump chambers or actuating plungers and regulation secured by dynamic balance of columns 16 and 16 For low pressures the blowing tubs situated at the ends of the play pipes 17 and 17 which are made of relatively large diameters toficorrespond with the large displacen'ients required. In certain. cases it even desirable to connect differential pistons operating in cylinders of the uni-flow type with inlets operated by said pistons and separate discharge outlets so placed as to avoid heat losses due to counterflow. Such an arrangement of uni-flow compressor cylinder is shown in Fig. VII. By proper arrangement it is entirely possible to use this combination to pump both elastic and non-elastic fluids at different pressures simultaneously or interchangeably.

Upon the arrangement and proportions of the reciprocating masses depend the characteristics and speed of operation of such apparatus. The working strokes, and the pressures due to weights of such columns and pressures of whatever medium acts above them, should be so designed that the proper amount of energy is stored and transmitted to compress'the contents of the power cylinders as nearly as possible to the pressure at which primary medium is supplied. Other conditions being then constant, the speed of operation will depend upon the relative lengths of the columns. The shorter the columns, and the greater their diameter, the quicker will be the period of reciprocation. Conversely, the longer and thinner the columns for a given power, the slower the speed. The total weight and length of each column is calculated to store, at allowable fluid velocities, suliicient kinetic energy to allow expansion in the power cylinder, and to perform the subsequent functions of pumping and compressing. Properly designed and constructed, each element of this combination benefits in a peculiar way by the characteristics of the other. The uniflow cylinder provides a reliable source of power at high efficiency while the Humphrey system of pumping and compressing utilizes most effectively the expansive energy, and by its momentum allows full expansion, and effects the high compression which, in turn, makes for high eificiency of the prime mover.

I am aware that it is not broadly new to utilize an expansive force for pumping and compressing by means of reciprocating masses consisting wholly or in part of fluids to be raised or forced. I do not claim the specific arrangements whereby dynamic pressures are utilized for discharge at high pressures, entrainment at low pressures, or regulation by dynamic balance, since those are the inventions of Charles G. Trump as described in his eopending application above referred to. I believe myself to be the first, however, to conceive the combination with these, and other arrangements, of that power cylinder which utilizes most effectively the expansive energy of a medium supplied at high pressure, such as steam.

What I claim is 1. The method of utilizing expansive energy, which consists in introducing steam into a cylinder end and exhausting it through a discharge removed from said end, controlling the discharge by a piston which uncovers the discharge at the end of its power stroke, maintaining the inlet end sufficiently hot to prevent initial condensation, and maintaining the discharge cold, utilizing the power stroke of the piston to cause one movement of reciprocation of a liquid column adapted to acquire useful momentum and utilizing a return stroke of the column to entrap and compress the expanded steam that has not been discharged from the cylinder.

2. The combination of a uni-flow steam cylinder having an inlet port in the head or end thereof, a live steam jacket on the head or inlet end of the cylinder, said cylinder having exhaust ports at a point removed from the inlet end, an elongated piston op erating therein, and adapted to uncover said ports at the end of its power stroke and quickly cover them on the return stroke and thereby to prevent cooling of the interior of the cylinder, a play pipe for the reciprocation of a column of liquid adapted to acquire useful momentum and means whereby the power stroke of the piston causes one stroke of reciprocation of the liquid column and the return stroke of the column causes 45 the piston to entrap and compress steam in the cylinder as it moves toward the hot head.

WM. CLINTON BROWN.

WM. 0. WALKER.

Copies of this patent may be obtained for five cents each, by addressing the Commissioner of Patents, Washington, D. G. 

